Fluid pressure engine



Feb. 22, v1955 C; 0, P KRAUSE 2,702,530

FLUID PRESSURE ENGINE Filed May 28, 1952 5 sheets-'sheet 1 Feb. 22, 1955 c. o. F. KRAUsE 2,702,530

FLUID 'PRESSURE ENGINE Filed May 28, 1952 5 Sheets-Sheet 2 l un l #un 3 R. *l N l M J U l A,l u W w l n l Q25@ l Qb w llnm, @h Nm, YT Q o N O N UIMM Feb. 22, 1955 c. o. F. KRAUsE 2,702,530

FLUID PRESSURE ENGINE Filed May l28, 1952 s sheets-sheet 5 ,www Sway United States Patent O FLUID PRESSURE ENGINE Christian Otto Federico Krause, Martinez, Buenos Aires, Argentina Application May 28, 1952, Serial No. 290,493

4 Claims. (Cl. 121-53) This invention relates to uid pressure engines and more particularly to a steam engine of the type comprising a plurality of cylinders of successively increasing diameters, inserted one into the other and wherein two consecutive cylinders have a common tangential contact generator.

One of the objects-of this invention is to provide a fluid, particularly steam, pressure engine, of the type having successively increasing-diameter cylinders inserted one into the other, each cylinder having a common point of tangential contact with the adjacent cylinders, wherein said cylinders are arranged so as to eliminate the dead center without the necessity of coupling two or more units in tandem.

A further object of this invention is to provide a lluid pressure engine having a higher capacity relative to the multiplicity of cylinders, than it is possible with engines of the known type.

A further object of the invention is to provide a fluid pressure engine which will be lighter in weight relative to the output thereof, with respect to engines of the known type.

A further object of this invention is to provide a lluid pressure engine which will be cheaper to construct than known engines of like output.

A still further object of the invention is to provide a fluid pressure engine which will produce a better thermal output, with respect to known systems.

A still further object of the invention is to provide a fluid pressure engine which will eliminate the torque on the drive shaft to which engines of the known type is subject due to the fact that the different cylinders responsive to the coupling in tandem on the drive shaft exert the turning effort on said shaft in different planes perpendicular thereto, Thus, a machine is provided wherein all the turning efforts are exerted in a single plane perpendicular to the drive shaft.

A further and important object of this invention is to provide a iluid pressure engine wherein the output may be increased without increasing the eccentricity of the cylinders and therefore without increasing the torque on the drive shaft.

With the aboveobjects in view, a fluid pressure engine, particularly a steam engine is provided starting from the principle of the French Drevet system but wherein the above technical drawbacks are overcome by fundamentally different means as shown hereunder:

Assume two circles having different diameters, the smaller one contained in the larger circle so that their circumferences will have a common point of tangential contact. In this case the line of the centers will pass through the tangential contact point and may be considered the ordinate axis of a system of coordinate orthogonal axes. The difference between the circular surfaces will be a crescent-shaped surface. A straight-line segment connects the two circumferences so that when it coincides with the Y axis it will also coincide with the direction of the radii of both circumferences, dividing the crescent-shaped surface in two parts of variable magnitude, depending on the position of the straight-line segment with respect to the crescent-shaped surface. When referred to volume the above may be defined as follows: v

Assume two hollow cylinders having different diameters, the smaller diameter cylinder contained in the larger one so that their cylindrical surfaces will have a point of tangential contact. The plane containing the 2,702,530 Patented Feb. 22, 1955 axes of the cylinders will also contain the point of tangential contact and may be considered the ordinate plane of a system of coordinate orthogonal planes. The difference in the volumes of the cylinders will be a volume which is crescent-shaped in cross-section; a plane segment connects the two cylindrical surfaces so that when it coincides with the ordinate plane it will also coincide with the radial plane of both cylinders, dividing the crescent cross-section volume in two parts of varying volume, depending on the position of the plane segment ICE .with respect to the crescent-shaped volume.

From the above it is possible to establish the following distinctive features of the engine of this invention as against the Drevet system.

The Drevet system applies the principle strictly as indicated above, requiring in order to make possible the rotary motion of the engine that the plane segment hereinafter called partition, be jointed to one of the cylinders, for example the smaller cylinder, and guided by a guide in the other cylinder across which it extends. Thus in the course of one turn the partition will take varying positions, intermediate the radial planes of the cylinders, due to the fact that same mean angular speed is obtained in both cylinders, although the tangential speeds will be different, in order to obtain the mutual rotation of the two cylinders on the tangential contact point eliminating substantially the friction between the two cylinders.

In order to eliminate the dead center effects a coupling arrangement is provided on a single shaft of two like cylinders with the eccentrics shifted at 180.

This invention contemplates the construction of an engine starting from a predetermined number of concentric hollow cylinders, the number of which is only limited by requirements in the practical application thereof, said cylinders being non-deformably joined to each other, and with the provision of a single radial partition, a cylinder which is eccentric with respect to those mentioned above being located between each pair of, cylinders. these eccentric cylinders may be mounted on a single i eccentric, in which case all the tangential contact points will be located in a single plane, such as for example, thel ordinate plane, or they may be mounted on different eccentrics distributed equiangularly on the engine shaft.

In the present case, and as a practical example, an

engine is contemplated having four concentric cylinders forming part of a series which is completed with a further series of three eccentric cylinders, mounted on eccentrics shifted at 180 from each other. The invention contemplates a minimum basic element capable of constituting an engine said basic element being formed by two concentric cylinders non-deformably joined to each other with a rigid partition, with a cylinder which is eccentric with respect to the rst two, inserted between said pair and with the two tangential contact points comprised in the same plane containing the xed axes of said pair of cylinders, i. e. the engine shaft and that of the eccentric mounted thereon. This basic element constitutes a complete unit having no dead centers and in its motion the rigid partition thereof is always contained in a radial plane of the concentric cylinders.

Therefore, starting from the point of tangential contact, each eccentric cylinder will have a varying angular speed on each revolution, which will be lower than that of the respective concentric cylinder in the first half-turn and higher in the second half-turn, whereas all of the concentric cylinders are made to rotate at the same angular speed.

This arrangement will produce the mutual sliding of the cylindrical surfaces when crossing the plane containing the tangential contact points causing the wear thereof by friction, but the latter will only occur during the engine adjustment period, since the elements insuring the position of the cylinders relative to the engine shaft will prevent further wear of the cylinders once the proper adjustment thereof has been obtained.

In case of acting as a prime mover under the action of a propelling fluid expandible at high pressure, the arrangement of a series of concentric cylinders and a series of eccentric cylinders, with axial inlet through the hollow shaft thereof, and in some of the modified embodiments thereof Vwith multipleexpansion and exhaust chamber surrounding the drive member or members, allows same to accumulate and maintain concentrated a great thermal mass whereby an assembly is obtained which will be very economical in operation due to the substantial increase in thermal output, as compared with the Drevet engine over which it also shows advantage. as re.- gards weight, space occupied thereby and cost of` con. struction, as a result of the smaller number of cylindrical bodies for the samenumber of. working chambers and power.

The above comparison showsthat while the engine of the present application and that of Drevet patent are based on the same principle, the. solution of technical problems which areY fundamentally differentare contemplated Vin `the former, and it will be. seenthat apart from the improvements mentioned above, the engine of this in vention affords a great fiexibility for operating as a high pressure or multiple expansiondriving engine, as will be seen from` the following description.

In order that the invention may be more clearly understood and readily` carried vout same has been illustrated by way of vexample in the accompanying drawings, in which:

Fig. l is a sideview ofthe engine, partly in section.

Fig. 2 is a front sectional viewA of the engine, taken along the lines I-I of Fig..l.

Fig.. 3 is an axial sectional. view of avmodied embodiment of theengine.

Fig. 4 is a front view showing the fixing in a predetermined .position ofone of theengine members, relative to a hand-controlled change-speed member.

Fig,l 5 isa perspective view of the portion of the engine relatingto two series of cylinders, one of four and the other of three cylinders.

Fig. 6 is a perspective view of the arrangement of two concentric cylinders and one eccentric cylinder connected by a radial partition.

In .accordance with. the above and with reference to the drawings,.the invention contemplates a rotary engine whichifsupplied with external mechanical power mayV be usedas a fluid drawing and driving machine of the lift-.arid-.force pump system, compressor and vacuum pump, andif supplied -with fluid under pressure will act as amechanical power generator, forming a motor unit operating by the difference in pressure between the in flow. and .outflow of the fluid which may be in a single physical state such as liquid,tvapor or gas, or a combination oftwo or even three physical states, performing in either case the function of driving two series of hollow cylinders forming the essentialfcomponents of the engine, the arrangement of which willbe described hereunder with reference to Figs. Sand 6 of the accompanying drawings.

Said Figs. 5 and 6 show a set of hollow cylinders formingy the first group, concentric with each other and with an.` axis a, and a complementary set ofvhollow` cylinders Z which are concentric with their respective axes b, parallel to each other and to the axis la (Fig. 5) and arranged along the generator of a theoretical cylinder c. Said cylinder'sforming the first groupare designated by the reference numeral l.

Each of the cylinders 2 of the second group, the number ofwhich may vary but assumed to be three in this instance merely by way of example, is inserted between each pair of .cylinders 1 inthe first group with which it is maintained in tangentialv contact relationnby one of the generatorslocatd at the points of intersection of a dia-` metrical plane' of' the cylindersv 1 in the firstgroup and withthe surfacesof the latter, the contact generators being held fixed since the axes la and b of both groups of cylinders arefixed and parallel to each other, although the actual generators of the cylinders lare successively replaced inthe position of tangential contact during the courseof one revolution.

The tangential contact generators constitute the actual points ofa'pplicatio'n of the resultant of the reactions to the motive force, which they later'transfer to the engineV shaft, caused by the'pressure exerted by the .fluid on a partition 3 `arranged along a radial plane of the cylinders 1 of the first group and rigidly secured thereto, onwhich each ofthe cylinders 2 of the second group inserted bef.

tweenY eachtwo' cylinders. 1 of the firstgroup willy slide. with the reciprocating motions duringfthe `course of one.,v 85

revolution.

The driving action caused by the rotary motion of the transmit such motion to the cylinders, thereby driving same, and the resultant of the reaction will pass through the engine shaft.

In order to facilitate the understanding of this invention, the following explanation will be limited to the fundamental element illustrated in Fig. 6, comprising two cylinders 1 inthe` first group and one cylinder 2 in the second group, rotating about their respective fixed parallel, axes a and b, and in order to simplify the description, the smaller-diameter cylinder in the first group will be referred to astheY inner cylinder, while the cylinder having the largest diameter in the first group will be referred to as the outer cylinder, said cylinders being concentric, whereas the eccentric cylinder of the second group, inserted between the two concentric cylinders will be referred to as the intermediate cylinder.

In` accordance` with the above and as shown in Fig. 6 of the drawings, thev concentric cylinders 1 of the first group determine an. annular space in which the eccentric cylinder-2 of the second group is inserted, said annular space. being divided in two sections d--d and e-e, the cylinders 1 of the first group being joined together, as mentioned above, by a radial partition 3 by means of which said sections corresponding to respective chambers are formed. Suitably guided by mechanical devices, the cylinders 1 of the firstgroup will only rotate about the axis a thereof, whereas the cylinder 2, also guided by other' devices, will only rotate about its axis b. The partition 3 will move together with the three cylinders, accompanying them in their rotary motion, but the lines of tangential contact will constantly remain at the theoretical. generators f and g contained in the plane containing also theA axes a and b. rl`his assembly is closed by two sealing plates or lids parallel to each other and perpendicular to the axes a and b.

If an expansible uid under pressure is forced through the orifices 4 and 5, the expansive force will act on one of the faces of the partition 3, the lower face in the embodiment shown in Fig. 6,v causing same to move in the rotary direction indicated by the arrows F in Fig. 5, carrying the assembly of cylinders in its movement. The chamber d comprised between the tangential contact generator g and the lower face of partition 3 will increase in volume as the partition is moved due to the expansive force of the fluid under pressure, whereas as zone of the chamber d comprised between the upper face of the partition 3 and the tangential contact generator g will decrease in volume. Similarly, the chamber comprised by the tangential contact generator f to the lower face of partition 3-will also increase in volume, while the volume of-the chamber comprised between the upper faceof the partition. 3 and the same tangential contact generatory f will decrease. It will thus be seen that the increasing volume chambers (the partition is moved away from the tangential contact generator) are those in which the corresponding face of thepartition 3 receives the action of thedi'iving fluid at the highest pressure, i. e., the inlet chambers or working chambers, and that the decreasing volume chambers (thepartition 3 moves towards the tangential contact generator) are those discharging the expanded fiuidV contained therein, i. e., the lower pressure fluid jfrom the previous'cycle, which is done through the orifices 6 and 7 shown in Fig. 6. Said cycles are successively repeated7 since a suitable mechanismy comprising a distribution valve, port jacket, inlet and exhaust cham.-

bers and orifices, will perform` their respective,functions` at the proper times within each period, regulating and adapting also the speed and power to the momentary resistances to be overcome. Actually, the concentric cylin.- dersl of the first group` are connected to theshaft, brackets, bearings and pulley (or fiange for direct coupling) for utilizing the power of the engine Wherever same is used.

It has 4already been mentioned above that the intermediate cylinder 2 of the second group dividesthe annular spacebetween the inner andouter concentric cylinders 1 of thefirst group intwo independent non-cern.- municating sections, the inner section nearest the axis of rotation being designated e-e, whereas the outer section removed therefrom is designated` 1 -d'.

The.. partition 3 driving the cylinder assembly in its rotary movement represents in, this engine the function of a piston in a reciprocating machine. In the latter, the

inner volume limited by me cylinder and the heads thereof is divided in two independent and non-communicating working chambers by the piston or partition, one of the faces of which will receive the pressure of the expansible uid driving and moving same, with the resulting increase in volume of the working chamber on that side of the piston and which in that period will be the drive chamber, the rectilinear movement of the piston and the rod thereof being converted into a rotary motion by means of connecting rods, cranks and the like. Similarly, in the engine of this invention the partition 3 will receive the force of the expansible fluid pressure on one of the faces thereof, moving same and increasing the volume of the chamber on that side, which in this period will be the drive chamber where the expansive force of the uid will drive the partition 3, causing same to carry therewith the rotary parts of the machine.

In Aboth the rotary and reciprocating engines, the chamber on the other side of the piston or partition and the volume of which decreases with the movement, constitutes at such time the uid exhausting chamber, but on the following period said exhaust chamber will become the driving chamber, and the driving chamber will become the exhaust chamber. It should be noted that in the above comparison a single cylinder in the reciprocating engine and a single crescent-shaped section in the present rotary engine has been assumed, but as mentioned hereinbefore, the latter has a minimum of two crescentshaped sections, thereby constituting the equivalent of a two-cylinder reciprocating engine but in which the output losses due to the conversion of the rectilinear movement into a rotary and the consequent friction of the parts used in this conversion, as well as the friction of the cylindrical surface of the piston with that of the cylinder have been eliminated.

lIf instead of two concentric cylinders the engine should comprise three concentric cylinders with two eccentric cylinders, it would be equivalent to a four-cylinder engine and, in general, if it has n concentric cylinders it will be equivalent to 2(n-l) cylinders. The example shown in Fig. 5 is thus equivalent to a six-cylinder engine.

Fig. 2 is a sectional View of the engine, taken along the line I-I in Fig. l. The latter has been depicted at an inlet point 45 ahead of Fig. 2 i. e., Fig. l shows the engine after rotating one-eighth of a turn more than the position shown in Fig. 2. This was done so as to show more clearly the travel of the uid from the admission through the inlet pipe to the working chambers, as will be seen hereinafter. inlet valve has been shown schematically in the middle of Fig. 1 as the only way of showing the direction of the conduits in a single plane.

By way of a pipe 8 (see Fig. 2) which is iiexible or provided with a ball joint allowing a longitudinal displacement of the order of 60 millimeters of pipe 9 in the direction of its axis, the fluid under pressure from the generator arrives at the nozzle 10 thereof through a straightway valve 11. The pipe 9 is screwed onto the central body of inlet valve 12, having secured to the front part thereof by means of coupling bolts and a ange, a stem 13 extending through the shaft 14, to the reversing hand-wheel 15 the coupling of all of said members, viz. pipe 9, valve 12, stem 13 and hand-wheel 15 forming a single unit capable of being moved longitudinally along the axis thereof but prevented from rotating by the parts 16, 17 and 18 serving as a guide therefor, the last two constituting the male and female members of a flat slide which is fixed in position by means of a conical latch 19 (Figs. 3 and 4). The front portion of part 18 serving as a guide for the hand-wheel 15 is formed by a circular head and a cylindrical body on which said part 18 is formed (Fig. 4). The assembly of hand-wheel 15, stem 20, valve 12 and pipe 9 is moved to the right or left (of the drawing) by pushing the hand-wheel 15 or pulling therefrom after the removal of latch 19 (Fig. 4) which should be inserted again in either of the holes 21 or 22 (Fig. 3) formed in part 18 and stem 13, thereby selecting the direction of rotation when the machine is used as a motor. Said part 18 is screw-threaded almost throughout its length, so that by means of nuts and check-nuts it may be iixed in position and provide the suitable tension to the regulating spring 33, tix the stroke limits for the distribution valve by means of members 24, 25 and 26, and also determine the position of part For the same purpose, the

6. 27 which together with parts 28 and 29 forni a centrifugal regulator which, actuated by the speed of the machine acting as a motor, will oppose to the sudden changes in operation, since in increasing or reducing the inlets of liuid under pressure it will automatically adjust the motive power to the instantaneous requirement thereof.

The mechanical device described above for moving at will the distribution valve has been designed in order to facilitate the practical location of the valve in its dijferent working points during the experimental tests, but it will be understood that same may be substituted by other devices which are more easily actuated in service and which may be either electrical, pneumatic, a combination of both, or the like.

The admission valve 12 is externally cylindrical and has formed on different planes normal to the axis thereof a pair of ellipsoidal openings 30 and 31, of variable section, serving for vdistributing the uid under pressure in the working chambers. Each of these openings will act in a running direction while the other one performs no function. When the opening 31 shown in Fig. 2 is working, the engine will rotate in the direction of the arrow F in Fig. 1, and it will rotate in the opposite direction when the valve 12 is shifted to the right in Fig. 2, to the point in which the opening 30 shown in full lines faces the corresponding port in the valve sleeve or case. In the central space of the cylindrical valve surface comprised between the two ellipsoidal openings, there is provided an opening 32 of circular crown shape serving to collect the driving fluid which should be discharged after having yielded all the usable power. This annular opening opens into the inner valve channels 33 leading the exhaust .lluid to the chamber 34 surrounding the inlet pipe 9 in the valve body, and from said chamber through openings 35 formed in shaft 36 the exhaust uid will pass into the space between the cylinders and the casing thereof, from where it is expelled through the lower elbow 37 or, in accordance with the embodiment shown in Fig. 3, the exhaust fluid will follow by the extension of chamber 34 to the exhaust pipe 38 carrying same outwardly.

Valve 12 is not a rotary valve and any generator of its cylindrical surface will always be on the came diametrical plane while the machine is operating since, as already indicated, the parts 19, 18 and 16 will prevent any rotary motion. By means of the guide member 16,

however, a slight rotary motion may be applied by hand to the valve so as to change the points where the admission starts and ends, which may be done by loosening the screws holding said member 16 in position and by means of the slides with which it is provided it may be turned clockwise or anti-clockwise, thereby changing the guiding position of the valve. By tightening again the screws fixing said member 16, the Valve will again be held against further rotary movements. Inasmuch as the member 16 is the valve holding means preventing the rotation thereof, it was designed so as to serve also for regulating and adjusting the distribution.

With the engine in motion, if the working load is constant, as well as the pressure of the driving uid, the valve will remain still. It will only be required to effect a slight rectilinear horizontal movement caused by the centrifugal regulator or governor, parts 28 and 27 and opposing spring 23 each time the operating speed is changed for any reason. Such movement will decrease or increase the driving fluid inflow, thereby modifying the 1percentage of expansion and regulating the engine wor The latter may be also obtained by means of a lever 29, with the same result as the centrifugal governor butV when desired by the operator, viz., it will regulate the steam inflow, increase or reduce the speed or stop the engine at will when so desired, without the lever and the governor interfering with each other, as it will be sucient to release the lever grip for same to return to the uncoupling position; however, if desired, it may continue to act by means of a small device holding same locked in the coupling position thereof.

The portion of the engine producing work, viz., the portion associated with the cylinders, will now be explained in detail. In order to facilitate the description, the portion having the actuating devices (left-hand portion in Fig. 3) will be referred to as the front portion, and the portion of the inlet pipe entering the machine rear portion.

'The-part-.40; compriseswhat has been designated inner cylinder-and outer cylinder (1f infFig. 6) and' the frontl cylinder cover. Within-the annular space'compri's'edbetween-the innerand outerA cylinders, there is housed.y an intermediate cylinder 2 (Fig. 6) 'which iseccentric with respect-tothe other two cylinders, the assembly` being closed bya rear cover 41. The plane faces of the ir1termediate cylinder 2 are tightly held against the inner faces ofthe cylinder covers.

Said part v40 is guided and iixed to shaft 14. and inner race of the ball-bearing 42, the axis a in Fig. 6 being the axis of rotation thereof.

The intermediate cylinder 2` will rotate about its own. axis b (Fig. 6) which is parallelandin unchangeable position relative to-the axis a, and sinee it is inclosed between the inner and outer cylinders and between the, cylin der covers, it is firmly guided vby four bolts 43 (Figs. l`

and y2)extendingthrough oval-shaped openings 44 formed inthe front and rear cylinder covers 40` and 41 and into the. intermediate cylinder 2, securing same to the front star flange 4 5 and thevv rear flange 46'y by means of the members VV47 and 48,y said flanges being supported by the ball-bearings49 and 50, the formerbeingseated on a xed eccentric stud 51 forming part of the front cover 52 of the casing, and the ball-bearing 50 on the eccentric stud 53 of the fixed rear shaft 36.

The oval-shaped openings 44 are closed by mirrortinished plates (of the atvalve type) forming part of the front star flange 45 and member 47,v said plates being permanently forced against the seats thereof Vby means of pins 43 and seat pressure regulating springs enclosed in sealing caps 48.

The location of the eccentrics 51 and 53 dening the position of the axis b relative to the axis a in Fig. 6, will'ldepend on the insertion of the key 54 in theproper point 2and, on theposition in whichl the casing frontl cover 52,4isV- placed.` Figs. land 2 show the eccentrics in the same `position indicated in Fig. 6, i. e., withthe axis b thereofon the same vertical diametrical plane, below the engine axis a. The ecentricity is determined so thaththe generators of the inner cylindrical surface of the intermediate cylinder will contact those ofthe inner cylinder of member 4() on the tangentialcontact generator 55 shownby a, double circle in Figs. l and 2, at the sameV time the generatorsof the outer cylindrical surface of the, sameA intermediate cylinder 2 contact those of the outercylinder of member 40 on Athe tangential contactgenerator 56 shown alsoV by a double circle in Figs. l and, 2. In view of the fact that the eccentrics 51-and 53 are` fixed, said contacts will take place constantly and invariably on thesarne verticaldiametrical planein the. tangential contact generators 55 and 56 (points f and g respectively in Fig. 6) which are xed even ,through the, entire assembly ofcylinders, cylinder covers and partitionl 8 inFig. 1 and 9. in Fig. 6 is rotating.

The central portion of the inner'concentric cylinder in memberAtlserves as a housing for a bushing or sleeve 57 having` a tightt thereinV and provided with four ports, twoof which, 58.V and 59, shown in full lines in Fig. 2, aremformedon` a singleplane normal to theaxisand shifted 180- from each other.

The .other two ports-60 andl are formed on a different plane.V parallel tothe previous one and also shifted 180 from eachother.

Thepiece 49. forming the inner and outer` concentric cylinders and the front cylinder cover, apart from the sleeve L57 which is detachable, is formed inthe body of theinner. cylinder, i. e., from the latter towards the axis, with. four. compartmentsV indicated at 62-63 in Fig. l and `.64. inV Fig. 2, and 65e-66 in Fig. 1 and 59 in Fig. 2, eachv openinginto a port in sleeve 57 and also into the cylinder drive and exhaust chambers. The compartments 65xandm66 in Fig. l correspond, in the` position shown, to the pressure fluid admission period for the direction indicatedby. the, arrow F', receiving the fluid delivered by the valve and leading same to the working chambers, i. e., directly.A to theuinnercharnber designated at 67 in Fig. l and68in Fig. 2, and throughL the pipe 71 to the outer chamber indicated at 69 in Fig. l and 70 in Fig. 6.

The other two compartments 72 and 73 are those receiving during that same period theuid already expanded, soasto discharge'same outV through thecentral annular channel 32 in valve 12:

It should be remembered that both the compartments 8.. andthe cylinder working and exhaust.` chambers perform the function mentionedabovel while'the lsame rotationall direction of the engine as indicated by the arrow. Fi is'- maintained, but that if the valve is shifted Sothat the engine will rotate inl the opposite direction, the func# tion of each compartment and working and exhaust charnber will be reversed, the admission chamber becoming an exhaust chamber andk vice-versa.

When the. engine isoperating as a mechanical power generator, the path followed bythe driving expansible.k

uid under pressurewill be as follows;

The fluid will arrive-at the engine through. the norzle` 10 of pipe 9, reaching the distribution valve which will remain stationary. With .the engine stopped, one.ofthe ports 58, 74, 60, 01161 in sleeve 57'will always Vbeconnected with the ellipsoidal inlet openings 30 or 31-in. valve 12, regardless of whether the engine is yprepared for rotating in one directionlor the` other, due tohaving set the distribution valvein either end position. It will thus be sucient to open thefluidstraightway valve. and the engine will start, asthere will be no.dead.cen. ters.

Upon reachingl the.,distribution valve, thedriving.v fluid.

revolution successively present one of the ports before..

the ellipsoidal opening inservice of the distribution valve 12 (which is stationary), through which the uid will pass to the correspondingy compartment62, 63, 65;-

or,66 and-thence to the cylindcrworking chamber readyv at that time for admission. When thefengine has ro tated through one-half `of a revolution, theiluid` willen?A ter the other port, passing into the respective4 compartment and thence into Vthe working chamber in theother cylinder.

The expanded fluid exhaust chambers will return 4the` fluid through the same compartments 62, 63, 6,5,l or 66 becoming exhaust compartments'in accordance with the, direction of rotation under consideration, to thefcentral exhaust channel 32 in valve 12(which will admit sarneA at all times and .regardless of the position of the ports)` and` thence through the exhaust lines 33 in saidv valve and the inner annular conduit 34V thereof, whereupon the fluid will pass (in the embodiment shown in Fig. 2) through the orifices 35 in shaft 36 tothe spacecorn.- prised between the rotary cylinder block andl the fixed casing thereof and thence to the external exhaustcn' duit through the lower elbow 37. Inthe. arrangement shown inFig. 3, the exhaust fluid will be discharged'. through the annular conduit 34 formed between thet in-fv let pipe 9 and the exhaust pipe 77 and supplementary.

pipes.

When the partition 8 (see Fig, 1) passes oppositerthe.4

contact'point 56 corresponding to the outerand interf mediate cylinders, the chamber which up to that mo-` ment vvasV an admission chamber will becomean. exhaust.v

chamber, and vice-versa, The same happens with thef` inner chambers when the partition passesopposite thev contact point corresponding to the intermediate and4 inner cylinders.

As may be seen from the drawings, the lubrication of the engine may be easily solved, and may be obtained-'byy means of ordinary lubricating cups tightly screwed for the. ball bearings, while for the inner partsof the machine an ordinary drop lubricator may be used.

The engine described above, operating with all the con-v trol devices freely movable, is rotary, of continuous exhaust, of controllable admission, reversible, of constant, speed. By blocking the centrifugal governor by meansof. d the hand device, it lwill operate as a variable speed reversible machine. By holding the reversing deviceidle it will act as a non-reversible constant speed engine. Byv holding the reversing device idle and blockingthe c'entrifff` ugal governor it willact as a non-reversible variable speed engine.

summarizing, this invention provides a fluid pressure engine, with differences 1n pressure, or the reversible type, which comprises a unit which in the embodiment shown in Fig. 5 is formed by series o? cylinders having successively increasing diameters, inserted one into the other, the innermost cylinder 1 in the first group having with respect to the outermost of said cylinders a tangential point h and i defining a substantiallly fluid-tight closure with the respective adjacent cylinder 2 of the second group, each of the intermediate cylinders in the second group having a tangential point j, k and l, m defining a substantially fluid-tight closure with each of the corresponding adjacent cylinders 2 of the second group while the alternate cylinders 1 of the first group counting from the innermost to the outermost cylinder are coaxial, and each of the slotted discontinuous cylinders 2 of the second group comprised between said alternate cylinders of the first group is eccentric with respect to said coaxial cylinders, with the respective axis b of each of said slotted cylinders of the second group preferably located in spaced angular relation along a single circumference concentric with the geometrical axis a of the cylinders in the first group, a continuous radial partition 6 being provided, connecting together all of the alternate cylinders of the first group, the edges of the slots 78, 79, 80 in each of said slotted discontinuous cylinders of said second group forming a substantially fluid-tight closure with said partition 6 by means of the joints 81 shown in Fig. l, capable of allowing an oscillating variation of the angle formed between the diametrical plan coinciding with the slot 78, 79 and 80 of the respective cylinder of the second group and the longitudinal plane of said partition 6, and allowing also the sliding of the edges of the slot 78, 79, 80 of the respective slotted cylinder of the second group on said partition 6, while the power transmission shaft 14 shown in Fig. 2 is fixed to the cylinders of the first group and coaxial with the geometrical axis a thereof.

While a specific embodiment of the invention has been described and illustrated, it will be evident that many changes, modifications and/or alterations will occur to those skilled in the art, without departing from the scope of the invention as clearly set forth in the appended claims.

I claim:

1. A fluid pressure engine of the variable pressure reversible type, which comprises a series of cylinders progressively increasing in diameter and inserted one into the other, the first and the last cylinders in said series having a point of tangency forming a substantially fluid-tight closure relative to the adjacent cylinders and all of the cylinders in said series having an individual point of tangency forming substantially fluid-tight closures to the fluid in the intermediate and adjacent cylinders, said series of cylinders being divided in two groups with each group containing at least two cylinders, the cylinders of the first group being arranged in alternate coaxial relation and the cylinders in the second group being arranged eccentrically and discontinuously relative to those in the first group and having the axes thereof in angularly spaced relation along a circumference concentric with the geometrical axis of the cylinders in said first group, a common connecting means between the cylinders in said first group arranged in sealing contact with predetermined points of the cylinders in said first group, together with auxiliary means forming guide joints for guiding the oscillating variation of the angle determined between the diametrical plane coinciding with the points on said second group cylinders and the longitudinal plane of said connecting means between the cylinders in said first group and, consecutively, the sliding of the contact points of said second group cylinders on said connecting means being provided with sealing means, side covers for the cylinders in said second group having openings provided with fluidtight closure means having a pin and slot connecting means for mounting said second group of cylinders.

2. A fluid pressure engine of the variable pressure reversible type, which comprises a series of cylinders progressively increasing in diameter and inserted one into the other, the first and the last cylinders in said series having a point of tangency forming a substantially Huid-tight closure relative to the adjacent cylinders and all of the cylinders in said series having an individual point of tangency forming substantially Huid-tight closures to the fluid in the intermediate and adjacent cylinders, said series of cylinders being divided in two groups with each group con- 10 taining at least two cylinders, the cylinders of the first group being arranged in alternate coaxial relation and the cylinders in the second group being arranged eccentrically and discontinuously relative to those in the first group and having the axes thereof in angularly spaced relation along a circumference concentric with the geometric axis of the cylinders in said first group, a common connecting i means between said first group cylinders arranged in sealing contact with predetermined points of the cylinders in said first group, together with auxiliary means forming guide joint for guiding the oscillating variation of the angle determined between the diametrical plane coinciding with the points of the cylinders in said second group and the longitudinal plane of said connecting means between said first group cylinders and, consecutively, the sliding of the contact points of the cylinders in said second group on said connecting means, said first group cylinders being provided with side covers, one of said covers being firmly secured to the engine power transmission shaft rotatingly mounted on the engine casing, and the other of said side covers being provided with pin and slot connections to form supporting means mounted in a freely rotatable manner on a member extending into said engine casing coaxially with the extension of said power transmission shaft, the cylinders inthe second group being angularly displaced with their eccentric axis 180 with respect to one another and the axis of said first cylinders.

3. A fluid pressure engine of the variable pressure reversible type, which comprises a series of cylinders progressively increasing in diameter and inserted one into the other, the rst and the last cylinders in said series having a point of tangency forming a substantially fluidtight closure relative to the adjacent cylinders and all of the cylinders in said series having an individual point of tangency forming substantially fluid-tight closures to the uid in the intermediate and adjacent cylinders, said series of cylinders being divided in two groups with each group containing at least two cylinders, the cylinders of the first group being arranged in alternate coaxial relation and the cylinders in the second group being arranged eccentrically and discontinuously relative to those in the first group and having the axes thereof in angularly spaced relation along a circumference concentric with the geometric axis of the cylinders in said first group, a common connecting means between said first group cylinders arranged in sealing contact with predetermined points of the cylinders in said first group, together with auxiliary means forming guide joint for guiding the oscillating variation of the angle determined between the diametrical plane coinciding with the points of the cylinders in said second group and the longitudinal plane of said connecting means between said first group cylinders and, consecutively, the sliding of the contact points of the cylinders in said second group on said connecting means, the mechanism of said engine being provided with an automatic centrifugal speed control device and main fluid inlet and exhaust conduits concentric with each other, the inlet conduit being internal with respect to said exhaust conduit.

4. A fluid pressure engine of the variable pressure reversible type, which comprises a series of cylinders progressively increasing in diameter and inserted one into the other, the first and the last cylinders in said series having a point of tangency forming a substantially fluidtight closure relative to the adjacent cylinders and all of the cylinders in said series having an individual point of tangency forming substantially fluid-tight closures to the uid in the intermediate and adjacent cylinders, said series of cylinders being divided in two groups with each group containing at least two cylinders, the cylinders of the first group being arranged in alternate coaxial relation and the cylinders in the second group being arranged eccentrically and discontinuously relative to those in the first group and having the axes thereof in angular spaced relation along a circumference concentric with the geometric axis of the cylinders in said first group, a common connecting means between said first group cylinders arranged in sealing contact with predetermined points of the cylinders in said first group, together with auxiliary means forming guide joint for guiding the oscillating variation of the angle determined between the diametrical plane coinciding with the points of the cylinders in said second group and the longitudinal plane of said connecting means between said first group cylinders 11- 12 and,4 consecutively, the sliding of. the Contact ypoints of` References Citedintheiile of this patent the. cylinders in Asaid secondv grouponsaid.. connecting means, side..covers for.said'engine,`an engine shaft,` the UNIfTEDSTATESlPATE-NTS mechanisml-of-said.enginebeingiprovided with an auto- 1,309,871 Allen July 15, 1919 matic.. centrifugal speed control device as av meansfor 5 1,682,564 Hill Aug.'28, 19218 determining the linear displacement ofV admission distributing. means. within resrictedflimits in responfse to FOREIGN PATENTS an increase. in rotation spee 1 and vice-versa, one o *saidl side coverslbeing connectedtothe engine, shaft, and a` 7245 Great Bntam Apr' 27 1891 main uidvinletand outlet concentric withl one another 10 4,147 Great Britain -f MR 16,71915 extending. through said. shaft. 

